DE202013007987U1 - Switching arrangement with a coupling and synchronizing device for a transmission (variant III) - Google Patents

Abstract

Shifting arrangement for a shiftable transmission (2), which has: - an input shaft (3), - a hollow shaft (1070) mounted on the input shaft with a first fixed gear (41) - a secondary shaft (62) with one on the secondary shaft (62) provided first idler gear (31) which is in engagement with the first fixed gear (41), - an external shift sleeve (1005) for the releasable form-fitting connection of the first idler gear (31) to the secondary shaft (62), the external shift sleeve (1005) is axially movable due to actuation between a first position and a second position, - a friction clutch assembly (1006) for connecting the input shaft (3) to the hollow shaft (1070), with a clutch axial actuation unit (1007), wherein the friction clutch assembly (1006) a releasable frictional connection of the input shaft (3), with the hollow shaft (1070), - an external shift sleeve axial actuation unit (1008) for the actuation of the external shift sleeve (1005), the clutch A Axial actuation unit (1007) and an external shift sleeve axial actuation unit (1008) are mechanically connected to one another, wherein the clutch axial actuation unit (1007) and the external shift sleeve axial actuation unit (1008) are further designed so that the friction clutch assembly (1006) is the frictional connection between the input shaft (3) and the hollow shaft (1029) after the external shift sleeve (1005) assumes the second position, and that the friction clutch assembly (1006) releases the frictional connection between the input shaft (3) and the hollow shaft (1029) before the external shift sleeve (1005) leaves the second position to assume the first position, and furthermore - a second idler gear (35) provided on the input shaft (3) which meshes with a second fixed gear (35), - an internal shift sleeve (5) for the releasable form-fitting connection of the second idler gear (35) with the input shaft (3), the internal shift sleeve (5) is axially movable between a first position and a second position due to actuation, - the friction clutch assembly (1006) producing a releasable frictional connection of the input shaft (3) with the internal shift sleeve (5), - an internal shift sleeve axial actuation unit ( 8) for actuating the internal shift sleeve (5), the clutch axial actuation unit (1007) and the internal shift sleeve axial actuation unit (8) being mechanically connected to one another, the clutch axial actuation unit (1007) and the internal shift sleeve axial actuation unit ( 8) are designed so that the friction clutch assembly (1006) establishes the frictional connection to the internal shift sleeve (5) after the internal shift sleeve (5) assumes the second position, and that the friction clutch assembly (1006) establishes the frictional connection of the internal shift sleeve (5) ) with the input shaft (3) releases before the internal shift sleeve reaches the second position ment to take the first position ...

Description

The application relates to a transmission for a motor vehicle.

Such transmissions are provided, for example, in the drive train of a motor vehicle in order to transmit the drive power of a drive unit, for example an electric motor or an internal combustion engine, to a driven running wheel.

The application specifies an improved and simplified shift arrangement for a transmission, a transmission, a drive train for a motor vehicle and a motor vehicle equipped therewith.

The switching arrangement according to the application has an input shaft, a hollow shaft mounted in particular on the input shaft with a first fixed wheel, and a secondary shaft with a provided on the secondary shaft first idler gear, which is in engagement with the first fixed gear.

An external shift sleeve provides a releasable positive connection of the first idler gear with the secondary shaft, wherein the external shift sleeve due to an operation between a first position, this corresponds to the position positively released or disengaged, and a second position, this corresponds to the position positively connected or . Indented, axially movable. A kinematic reversal of these two positions is conceivable.

Further, a friction clutch assembly for connection to the input shaft is provided with the hollow shaft, which has a clutch Axialbetätigungseinheit or Reibschlussbetätigungseinheit, wherein the friction clutch assembly makes a releasable frictional connection of the input shaft with the hollow shaft.

An external shift sleeve axial actuation unit is used to actuate the external shift collar, wherein the clutch axial actuation unit and the external shift sleeve axial actuation unit are mechanically or not coupled to each other, rather than hydraulically or electrically.

The clutch axial actuation unit and the external shift sleeve axial actuation unit are further configured such that the friction clutch assembly establishes the frictional engagement between the input shaft and the hollow shaft after the external shift sleeve assumes the second position and the friction clutch assembly controls the frictional engagement between the input shaft and the input shaft Hollow shaft releases before the external shift sleeve leaves the second position to take the first position.

This design ensures a simple function, with a little complex operation is provided. The mechanical coupling of the clutch axial actuator and the external shift sleeve axial actuator ensures high reliability of this external subassembly of the assembly.

In addition, an internal subassembly of the arrangement is still provided which has a rotatably provided on the input shaft second idler gear, which is in engagement with a second fixed gear. This second idler gear can also be designed as a further fixed gear provided on the input shaft hollow shaft. The second fixed gear can sit on the same auxiliary shaft as the first idler gear, it can also be arranged on another secondary shaft, which is arranged in particular parallel to the input shaft.

Further, an internal shift sleeve for releasably positive connection of the second idler gear to the input shaft and the hollow shaft is provided, wherein the internal shift sleeve due to actuation between a first position, this corresponds positively closed, and a second position, this corresponds positively connected, axially is mobile. A kinematic reversal of these two positions is conceivable.

In this case, the friction clutch assembly produces a releasable frictional connection of the inner disk carrier with the internal shift sleeve. An internal shift sleeve axial actuation unit is provided for operating the internal shift collar, wherein the clutch axial actuation unit and the internal shift sleeve axial actuation unit communicate mechanically rather than hydraulically or electrically. The clutch axial actuating unit and the internal sliding sleeve Axialbetätigungseinheit are also designed so that the friction clutch assembly makes the frictional connection to the internal shift sleeve after the internal or external shift sleeve takes the second position or is moved from the first position to the second position, and that the friction clutch assembly releases the frictional engagement of the internal shift sleeve with the sleeve before the internal shift sleeve exits the second position to assume the first position or move from the second position to the first position.

This design ensures a simple function, with a little complex operation is provided. The mechanical coupling of coupling Axial Actuator and Internal Shift Sleeve Axial Actuator ensures high reliability of this internal subassembly of the assembly.

The internal subassembly of the assembly and the external subassembly of the assembly and the external selector sleeve axial actuator and the internal selector sleeve axial actuator are mechanically, and not hydraulically or electrically, directly or indirectly connected to each other such that the internal selector sleeve in the second Position is when the external shift sleeve is in the first position, and vice versa.

In a particular embodiment, therefore, the friction clutch connects both the input shaft and the internal shift sleeve simultaneously with the input shaft. The clutch axial actuation unit, the external shift sleeve axial actuation unit, and the internal shift sleeve axial actuation unit are mechanically, and not directly or indirectly, hydraulically or electrically interconnected, for example, by an idler gear so that they operate synchronized with each other.

For this purpose, each shift sleeve Axialbetätigungseinheit have a shift drum and a guided in a control groove of the shift drum shift pin. If the clutch Axialbetätigungseinheit has a pivotable or rotatable actuating element, wherein the switching pin is connected to the pivotable actuating element, then there is a very simple embodiment of the mechanical coupling. The shift sleeve Axialbetätigungseinheit and the actuator are, for example via a toothing engaged with each other, but there are also other direct or indirect mechanical couplings via other transmission elements such. As gears, chains or timing belt conceivable.

In particular, the internal shift sleeve axial actuation unit has an internal shift drum and an internal shift pin guided in an internal control groove of the internal shift drum. The clutch Axialbetätigungseinheit has a pivotable or rotatable actuating element, wherein the internal shift pin is connected to the pivotable, and rotatably smaller than 360 °, actuator. The internal Schaltpin can therefore be attached to the actuator, or made with this one piece. This is part of the concrete design of the mechanical coupling between the clutch axial actuation unit and the internal shift sleeve axial actuation unit.

Likewise, the external shift sleeve Axialbetätigungseinheit having an external shift drum with an external cam and a guided therein external shift pin, wherein the external shift drum or the external shift pin via a toothing with the actuating element is engaged, d. H. directly or indirectly via further transmission elements such. As gears, chains or timing belt is connected.

It can be provided an idler, which is driven by an actuator such as an electric motor with worm drive and which is coupled to the shift drum, wherein the idler gear is rotatably engaged via a toothing with the actuating element.

In the present application, the terms "rotatable" and "pivotable" are taken as synonyms, and the term "pivoting" can also be used to designate a rotation smaller than 360 °.

The actuator has, for example, a thrust bearing, which is provided for support in the axial direction on a housing part.

The external shift sleeve axial actuation unit and / or the internal shift sleeve axial actuation unit may be configured such that a first portion of the external control cam of the external shift drum extends circumferentially in a first axial portion of the external shift drum and that a second portion of the external or internal cam groove of the external or internal shift drum extends in the circumferential direction in a second axial portion of the external or internal shift drum, so that depending on a pivoting direction of the actuating element movement of the external or internal shift sleeve in a first axial direction or a movement of the external or internal shift sleeve takes place in a second axial direction.

The shift sleeve can thus be axially movable, for example, due to an operation between the first position and a third position - corresponding to a position "positively connected", wherein in the second position, a first idler gear is positively connected to the shift sleeve and wherein in the third position a second idler gear is positively connected to the shift sleeve. Thus, a shift sleeve can switch two idler gears.

Depending on a pivoting direction of the shift drum is then carried out a movement of the shift sleeve in the second position or in the third position. This causes the sliding sleeve in a pivoting of the actuating element in a first pivoting in a moves first axial direction and that the sliding sleeve moves in a second, opposite to the first pivoting direction pivoting direction in a second axial direction, which is opposite to the first axial direction at a pivoting of the actuating element. The slope of the first portion of the control groove in the circumferential direction can then be equal to the slope of the second portion of the control groove, so that there is a symmetrical operation. In this case, the slope will be the same sign in both axial sections, while the amount of the slope may be the same or different.

Thereby, a shift arrangement can be provided in which the clutch axial actuation unit and the shift sleeve axial actuation unit are designed so that the friction clutch assembly makes the frictional connection from the input shaft to the shift sleeve after the shift sleeve assumes a third position or from the first position into one third position is moved, and that the friction clutch assembly releases the frictional engagement of the shift sleeve with the input shaft before the shift sleeve leaves the third position to take the first position, d. H. moved from the third position to the first position. This results in a neutral position in the first position and two different switching positions in the second and third positions for coupling two different idler gears to the input shaft.

The first axial section and the second axial section of the relevant control groove are respectively followed by clutch actuating sections, by means of which the respective shift sleeve is not displaced axially, but an actuation of the clutch axial actuating unit takes place. In other words, the mechanical coupling between the axial clutch actuation unit and the respective shift sleeve Axialbetätigungseinheit is designed such that when the contour of the relevant control groove for the relevant shift sleeve has an axial extent, the contour for the clutch actuation has no axial extent, and vice versa.

There is a direction of rotation independent actuation of the clutch device in both switching operations. The clutch is only "turned on" in a single direction while the shift drum in question can operate the shift sleeve in two directions.

The internal shift drum of the internal shift sleeve Axialbetätigungseinheit is mounted axially fixed and rotatable in the circumferential direction on the internal shift sleeve. As a result, the respective internal shift sleeve is rotatable with respect to the relevant internal shift drum, wherein the shift drum is axially enclosed by the internal shift sleeve. It lies in the axial direction on lateral stops of the internal shift sleeve, wherein the internal shift drum in the circumferential direction on the internal shift sleeve can slide.

The internal shift drum of the internal shift sleeve Axialbetätigungseinheit has an external rotational definition in the form of a toothing or a spline, which is provided for support on a corresponding toothing or spline of a stationary housing part. For supporting on a stationary housing part thus serves a complementary design, such as a spline. This ensures a rotational anchoring of the respective internal shift drum on the housing part with simultaneous axial mobility. As a result, the interaction is further ensured that with axially fixed and rotatable freely movable actuator via the switching pin in conjunction with the rotationally fixed and axially movable shift drum, the shift sleeve can be moved axially.

In one embodiment, the external shift drum is freely rotatable and axially fixed. In the external control groove of the external shift drum, an external Schaltpin or SchaltSchaltpin is guided, which can be connected to a shift fork or - via a selection device - selectively with one of a plurality of shift forks. This embodiment may entail a simple embodiment of the selection device. In a kinematic reversal to the external shift drum may also have an external rotational fixing or fixing, for example, a toothing or a spline, which is supported on the housing side. For supporting on a stationary housing part serves a complementary design, such as a spline. This ensures a rotational anchoring of the external shift drum on the housing part with simultaneous axial mobility, whereby it can move axially. The external shift pin is then formed so that it is axially fixed relative to the transmission housing and thereby can move in rotation relative to the external shift drum.

The external shift sleeve axial operation may include a shift drum with cam groove and a shift pin guided in the cam groove. The shift drum can be rotationally free and axially fixed, the shift pin is axially free and rotationally guided, or vice versa. The first embodiment is used more frequently than the second embodiment, because this brings benefits for vehicle transmission with it, in particular with regard to the limited axial space there. In both embodiments, the rotatably movable element is connected to the intermediate wheel and it is driven by this. The axially movable element is connected to a shift fork which in turn axially actuates a shift collar in communication with the shift fork.

In one embodiment, one and the same external shift drum actuates the same external shift sleeve in two directions. In another embodiment, the same external shift sleeve may be moved on the secondary shaft from a first external shift drum in a first direction and moved by a second external shift drum in a second direction. It can be additionally provided a selection mechanism so that a shift drum can actuate several shift sleeves.

According to the application, the friction clutch assembly has a multi-plate clutch which has a clutch pot or first outer plate carrier in communication with the input shaft. In addition, an associated with the shift sleeve second inner plate carrier and in a further embodiment, an additional clutch output shaft is provided, and a package of recorded in the first or outer disc carrier first outer disc, a package of recorded in the second or inner disc carrier second inner disc and a printing plate. In the following, the terms first and second plate carriers are used, so that the description also includes their kinematic reversal of "inside" and "outside". A first plate carrier in the description and the claims can thus stand for both the outer and for the inner plate carrier. Likewise, a second plate carrier in the description and the claims stand both for the outer and for the inner plate carrier.

The clutch Axialbetätigungseinheit is designed as a clutch actuator, in addition to the pivotable or rotatable actuator with an actuating teeth, such as an external toothing, arranged in the range of pressure plate and actuator actuating contour or a wedge-shaped actuating portion and a cooperating with the actuating contour actuator body for actuation having the pressure plate. The actuating body may for example be a rolling element, such as a ball, a cylinder or a stationary element. This design ensures in a simple manner that the pressure plate due to actuation of the actuating body by the actuating element compresses the outer plates and the inner plates and thus produces a frictional connection.

Frequently, a thrust bearing between the friction clutch assembly and the clutch Axialbetätigungseinheit is provided, wherein the pressure plate may also have a bearing surface of a rolling element of the thrust bearing.

The actuating contour is provided in a first embodiment in the opposite of the pressure plate tread of the thrust bearing, wherein the actuating body are then mounted axially fixed but rotatable about itself in the actuator. In another embodiment, the actuating contour is provided in the gear housing or attached thereto, wherein the actuating body are then arranged axially displaceably or radially and tangentially in the actuating element.

As an actuating body or rolling elements both balls and rollers are conceivable, wherein in the case of balls each associated raceways correspond to the spherical shape and wherein in the case of rollers each associated raceways correspond to the roller shape. A roller can interact with an axial ramp.

If the actuating body axially seated in the actuator, then the contour or the operating contour or the ramp or groove on a pressure plate opposite side of the thrust bearing and thereby facing the respective actuating body, wherein the actuating contour or the ramp fixed as such rotationally and is axially free to move. Conversely, if the Betätigungsigunskontur is provided on a side opposite the pressure plate side of the actuating element, for. B. on the gear housing, then the actuator body in the actuator are axially movable form, so that the lifting movement of the actuator body can act on the pressure plate. If the actuating contour is seated in the opposite face of the thrust plate of the thrust bearing, then this Betätigungsigunskontur is axially movable perform, but set rotationally with respect to the gear housing.

The actuating contour is further formed so that it has an axial extent in the circumferential direction, so that as a result of the rolling of the actuating body in the circumferential direction, the actuating body undergo an axial displacement. Thus, the axial extent of the actuating contour and the actuating body can be changed together by a movement of the actuating body in the circumferential direction. In this case, the actuating contour seen in the circumferential direction may be formed symmetrically to an axis which corresponds to a neutral position of the clutch actuating unit. Regardless of a symmetry of the actuating contour must be ensured in any case, that the actuating contour in both circumferential directions of a Center position or neutral position extends in the same axial direction.

The actuating contour can be formed both in the region of the actuating element and in the region of the pressure plate. The geometry of the contour depends on the actuator body. In the case of a sphere one sees a groove adapted to the ball, in the case of a roller one sees a ramp.

The wedge-shaped actuating portion may also be formed as an axially wedge-shaped actuating portion having a ramp formed on the pressure plate or on the actuating member. The actuator body are then linear or according to a local elastic flattening under load area on the actuating contour. The actuating contour thus has a depression or elevation, which is shaped to match the actuating body. That could be z. Example, be achieved by an actuating contour, wherein a longitudinal extension of the actuating contour has a cross section corresponding to a region of a cross section of an actuating body.

The switching arrangement has at least two, for example, three actuator body. It can also be provided a plurality of actuator body, these can then be arranged evenly spaced from each other. For example, then adjacent ramps or wedge-shaped grooves are provided which act on the actuating body, which in the circumferential direction z. B. are spaced from each other by 120 degrees.

The actuating body can be mounted on axles, wherein the axes are connected to the actuating element. It is grateful a ball with wedge-shaped groove, which serves as a raceway for the actuators whose contour corresponds to the contour of the ball. A roller can interact with an axial ramp.

If the actuating body axially seated in the actuator, then the contour or the operating contour or the ramp or groove on the opposite side of the thrust plate of the thrust bearing is provided, which is rotationally fixed as such. Conversely, when the contour or the ramp or groove is provided on the opposite side of the printing plate of the actuating element, for. B. on the gear housing, then the actuating body are axially movable form, so that the lifting movement can be on the printing plate. If the contour is seated in the opposite of the pressure plate tread of the thrust bearing, then this is to perform axially movable, but set rotationally relative to the gear housing.

The actuating contour is further formed in particular as a radially wedge-shaped actuating region, in which the axial extension of the actuating contour and the actuating body can be changed together by a movement of the actuating body in the circumferential direction. In this case, the actuating contour seen in the circumferential direction may be formed symmetrically to an axis corresponding to a neutral position of the clutch actuating unit, in particular due to the different axial extent of the actuating contour in the circumferential direction.

In a further development of the subject of the application, an actuator, in particular an electric motor for actuating the clutch Axialbetätigungseinheit and for actuating the shift sleeve Axialbetätigungseinheit is provided. This can be done so that a gear, which is provided on an output shaft of the electric motor, engages in a gear which is connected to the shift drum, which in turn engages in a toothing on the actuating element.

To increase the number of shiftable gears, a second external shift sleeve may be provided for further loose wheels on the secondary shaft or the secondary shafts, wherein the switching arrangement for the second external shift sleeve has a shift fork preselector actuating device, either the first external shift sleeve or second external shift sleeve with the external shift sleeve Axialbetätigungseinheit connects. In this case, the shift preselection actuating unit may have a first region for connection to a first shift fork, which engages in the first shift sleeve, and additionally a second region for connection to a second shift fork. The shift fork preselector actuator unit then has a first position in which the shift sleeve axial actuation unit is connected to the first shift fork, and a second position in which the shift sleeve axial actuation unit is connected to the second shift fork.

The number of positions of the shift fork preselection actuator units corresponds to the number of shift sleeves that actuates them.

In one particular embodiment, one end of the input shaft can have a first internal switching arrangement with a first internal switching sleeve, and at the other end of the input shaft a second internal switching arrangement with a second internal switching sleeve can be provided. This allows a compact design of the transmission with a large number of gears.

The application also relates to a shiftable transmission comprising a transmission housing, an input shaft, a hollow shaft mounted in particular on the input shaft with a first fixed gear, a secondary shaft with a first idler gear provided on the secondary shaft engaging with the first fixed gear, and a shifting assembly such as has described above. In the following, the terms "first idler gear", "first fixed gear", "second idler gear", "second fixed gear", etc. are to be understood generically, thereby encompassing a plurality of gear structures that can be combined with the subject matter of the application.

This is provided in mechanically coupled manner, a releasable positive connection of the first idler gear with the secondary shaft and a releasable frictional connection of the input shaft with the hollow shaft. The mechanical coupling is designed so that the frictional connection between the input shaft and the hollow shaft is made after the positive connection of the first idler gear is made with the secondary shaft, and wherein the frictional connection between the input shaft and the hollow shaft is released before the positive connection of the first idler gear is solved with the secondary shaft.

The shiftable transmission additionally has a second idler gear, which is provided on the input shaft or on the hollow shaft and which engages with a second fixed gear. The second fixed wheel can sit on the same or another side shaft as the other wheels, but also on another side shaft. The switching arrangement is provided for the mechanically coupled releasable positive connection of the input shaft to the second idler gear and for the releasable frictional connection of the input shaft to the second idler gear. The mechanical coupling is designed so that the frictional connection between the secondary shaft and the second idler gear is made after the positive connection of the second idler gear is made with the secondary shaft, and that the frictional connection between the input shaft and the second idler gear is solved before the positive connection of the input shaft is released with the second idler gear.

The mechanical coupling is in particular designed so that the positive connection of the first idler gear is made with the secondary shaft when the positive connection of the input shaft is solved with the second idler gear, and vice versa.

In a further development, a second idler shaft which is mounted in particular on the input shaft and has a third fixed wheel, a third idler gear which is provided on a secondary shaft and which engages with the third fixed wheel, and a second such shifting arrangement are also provided. The switching arrangement is used for mechanically coupled to each other detachable positive connection of the third idler gear with the secondary shaft, and for releasably frictionally connecting the input shaft with the second hollow shaft, wherein the mechanical coupling is formed so that the frictional connection between the input shaft and the second hollow shaft is made After the positive connection of the third idler gear is made with the secondary shaft, and wherein the frictional connection between the input shaft and the second hollow shaft is released before the positive connection of the third idler gear is solved with the secondary shaft.

The mechanical coupling is also designed so that in a first case the positive connection of the first idler gear is made with the secondary shaft when the positive connection of the input shaft is solved with the second idler gear, and the positive connection of the third idler gear is solved with the secondary shaft , In a second case causes the mechanical coupling, that the positive connection of the first idler gear is solved with the secondary shaft when the positive connection of the input shaft is made with the second idler gear, and the positive connection of the third idler gear is solved with the secondary shaft. In a third case causes the mechanical coupling, that the positive connection of the first idler gear is solved with the secondary shaft when the positive connection of the input shaft is solved with the second idler gear, and the positive connection of the third idler gear is made with the secondary shaft. Of course, the above cases apply vice versa.

According to a further embodiment, the shiftable transmission has a fourth idler gear provided on the input shaft or on the hollow shaft, which meshes with a fourth fixed wheel, which can both sit on the same auxiliary shaft as the other wheels, but also on another auxiliary shaft. The switching arrangement described above is provided for the mechanically coupled releasable positive connection of the input shaft with the fourth idler gear and for the releasable frictional connection of the input shaft with the fourth idler gear. The mechanical coupling is formed so that the frictional connection between the input shaft and the fourth idler gear is made after the positive connection of the fourth idler gear is made with the secondary shaft, and that the frictional connection between the input shaft and the fourth idler gear is solved before the positive connection of the input shaft is released with the fourth idler gear.

The mechanical coupling is further formed so that according to a first case, the positive connection of the first idler gear is made with the secondary shaft when the positive connection of the input shaft with the second idler gear is released, and when the positive connection of the fourth idler gear solved with the secondary shaft is. In this case, according to a second case, the positive connection of the first idler gear is solved with the secondary shaft when the positive connection of the input shaft is made with the second idler gear, and when the positive connection of the fourth idler gear is solved with the secondary shaft. According to a third case, the positive connection of the first idler gear is solved with the secondary shaft when the positive connection of the input shaft with the second idler gear is released, and when the positive connection of the fourth idler gear is made with the secondary shaft, which cases apply in reverse.

Depending on the rotational / pivoting direction of an actuating element of the switching arrangement, either the first or outer or the internal or second shift sleeve or positive clutch is engaged in unilaterally acting circuit. Thus, either the first or the second idler gear is connected to the friction clutch assembly, whereas the arranged on the input shaft hollow shaft is permanently connected to the output side of the friction clutch assembly. This permanent connection is made for example by a sleeve, which in the sectional view of 1 like a narrow bridge appears. The frictionally engaged clutch, on the other hand, is engaged in both directions upon pivoting of the actuating element, namely - due to a mechanical coupling between the frictionally engaged and the positive clutch due to the geometry or contour for the clutch actuation - in each case after the form-locking clutch has been engaged.

In a further embodiment, the transmission may comprise a first shift arrangement and a second shift arrangement, wherein the hollow shaft of the first shift arrangement and the hollow shaft of the second shift arrangement are arranged on the one common input shaft, and wherein the first idler gear and the second idler gear of the first shift arrangement respectively loose wheels the first and the third gear are, and wherein the first idler gear and the second idler gear of the second shift assembly are each loose gears of the sixth and fourth gear, and further wherein the internal shift sleeve of the first shift assembly operates analogous to the internal shift sleeve of the second shift assembly.

Such a transmission essentially corresponds to a six-speed transmission 1 but without the second secondary shaft and without the gears of the third and sixth gears. If no second secondary shaft is provided, then in a four-speed gearbox, the gear of the third gear must mesh with a fixed gear of the first secondary shaft. But then the output pinion would have to 1 to be moved slightly to the left. Similarly, a five-speed transmission or a six-speed transmission can be built.

An exemplary six-speed transmission having a first and a second shifting arrangement has an input shaft, a second hollow shaft, a first auxiliary shaft and a second auxiliary shaft, wherein the first shift arrangement and the second shift arrangement are arranged on a common input shaft, wherein the first idler gear and the second Losrad the first shift each Losräder of even gears are, and wherein the first idler gear, the second idler gear of the second shift arrangement are each loose wheels of odd gears, and wherein the first idler gear of the first shift assembly and the first idler gear of the second shift assembly operable by a common shift sleeve which is the first shift sleeve of the first shift arrangement and at the same time the first shift sleeve of the second shift arrangement.

Further features of such a transmission are the second idler gear of the shift assemblies, each of which is in engagement with a fixed gear on a secondary shaft. The operation of the shift sleeves on the shift drum is synchronized so that the first idler gear is connected to the secondary shaft when the second idler gear is released and vice versa. The actuation of the two switching arrangements is synchronized so that a load circuit takes place. First, the actuator of the shift assembly of the new gear is turned so far that the idler gear of the new gear is positively connected, then the friction clutch of the shift assembly of the current gear is released while the friction clutch of the shift assembly of the new gear is actuated, then the idler gear of the previously inserted Gangs solved. In this case, the synchronization of the two switching arrangements with each other can be realized both mechanically and electronically. Wear of the friction clutches z. B. be compensated by an electronically controlled adjustment of the angle of rotation.

Furthermore, in each case a further fixed wheel can be arranged on the hollow shaft. Thus, greater freedom in the choice of translations is possible.

Other gears are possible if additional gears are mounted on the hollow shaft or the idler gear arranged thereon. Then also more shift forks are needed.

A powertrain of the application has a transmission according to the preceding embodiments, wherein at least one drive shaft or propeller shaft of the drive train is connected to an output shaft of the transmission. Often this is done via an intermediate differential gear.

In a motor vehicle then the drive train is arranged so that an impeller of the motor vehicle is connected to a wheel drive shaft of the drive train.

The application will now be explained with reference to the accompanying figures.

1 shows a view of a transmission with mechanically coupled coupling and synchronizing devices of a switching arrangement according to an embodiment of the invention,

2 shows a partial view of a mechanically coupled coupling and synchronizing device according to 1 .

3 shows shift positions "1" to "5" of an external shift pin in an external control groove of a peripheral portion of an external shift drum of an external shift sleeve axial drive unit,

4 shows shift positions "1" to "5" of an internal shift pin in an internal cam groove of a peripheral portion of an internal shift drum of an internal shift sleeve axial drive unit,

5 shows a plan view of a ramp structure of a clutch axial actuation unit,

6 shows a cross section through the clutch Axialbetätigungseinheit according to 4 .

7 shows the shift position "1" of the external shift pin in the external cam groove of the peripheral portion of the external shift drum of the external shift sleeve axial drive unit,

8th shows the shift position "1" of the internal shift pin in the internal cam groove of the peripheral portion of the internal shift drum of the internal shift sleeve axial drive unit,

9 shows the top view of the ramp structure of the clutch axial actuation unit in the shift position "1",

10 shows the cross section through the clutch axial actuating unit in the switching position "1" according to 8th .

11 shows the shift position "2" of the external shift pin in the cam groove of the peripheral portion of the external shift drum of the external shift sleeve axial actuator,

12 shows the shift position "2" of the internal shift pin in the cam groove of the peripheral portion of the internal shift drum of the internal shift sleeve axial drive unit,

13 shows the top view of the ramp structure of the clutch axial actuation unit in the shift position "2",

14 shows the cross section through the clutch axial actuating unit in the switching position "2" according to 12 .

15 shows the shift position "3" of the external shift pin in the cam groove of the peripheral portion of the external shift drum of the external shift sleeve axial drive unit,

16 shows the shift position "3" of the internal shift pin in the cam groove of the peripheral portion of the internal shift drum of the internal shift sleeve axial drive unit,

17 shows the top view of the ramp structure of the clutch axial actuation unit in the shift position "3",

18 shows the cross section through the clutch axial actuating unit in the switching position "3" according to 16 .

19 shows the shift position "4" of the external shift pin in the cam groove of the peripheral portion of the external shift drum of the external shift sleeve axial actuator,

20 shows the shift position "4" of the internal shift pin in the cam groove of the peripheral portion of the internal shift drum of the internal shift sleeve axial drive unit,

21 shows the top view of the ramp structure of the clutch axial actuation unit in the shift position "4",

22 shows the cross section through the clutch axial actuating unit in the switching position "4" according to 20 .

23 shows the shift position "5" of the external shift pin in the cam groove of the peripheral portion of the external shift drum of the external shift sleeve axial actuator,

24 shows the shift position "5" of the internal shift pin in the cam groove of the peripheral portion of the internal shift drum of the internal shift sleeve axial drive unit,

25 shows the top view of the ramp structure of the clutch axial actuation unit in the shift position "5",

26 shows the cross section through the clutch axial actuating unit in the switching position "5" according to 20 .

27 shows a diagram with the course of the axial movement of an external or internal shift sleeve compared to the course of an axial force acting on an actuator when inserting a gear,

28 FIG. 12 is a graph of torque transfer when changing from a first friction clutch assembly to a second friction clutch assembly and the course of release and engagement of gears associated with the first and second friction clutch assemblies; and FIG

29 shows a switching arrangement according to a second embodiment of the invention

30 shows a motor vehicle with an engine and a drive train, which cooperates with a differential gear.

1 shows a switching arrangement 101 for a transmission 2 , with a first mechanically coupled coupling and synchronizing device 1001 and a second mechanically coupled clutch and synchronizer 2001 ,

The switching arrangement 101 is in a gearbox 28 arranged and has an input shaft 3 with a symmetry axis 57 on. The input shaft 3 is in the case 28 in a ball and roller bearing 26 as a fixed bearing and a roller bearing 27 stored as a floating bearing. The input shaft 3 indicates a first end area on the left side of the drawing 1004 and on the right side of the drawing, a second end region 2004 on.

The gear 2 also has a first secondary shaft 62 and a second spur 67 on, parallel to the input shaft 3 are arranged.

Reference numerals of like components of 1 that are in the area of the first end area 1004 and in the area of the second end region 2004 are arranged, differ by a system that follows a symmetry in the arrangement. The first digit of the four-digit reference sign has a "1" if the component concerned is in the region of the first end region 1004 is provided, while the first digit of the four-digit reference sign has a "2", if the component concerned in the region of the second end portion 2004 is provided. The third and fourth digits of the reference numerals of these components are the same.

Reference numerals of like components of 1 that are in the range of the first secondary wave 62 and in the area of the second secondary shaft 67 are also different by a scheme that follows a further symmetry in the arrangement. The second digit of the four-digit reference sign has a "0" if the component in question is in the range of the first secondary shaft 62 is provided, while the second position of the four-digit reference sign has a "5", if the component concerned in the second secondary shaft 67 is provided. The third and fourth digits of the reference numerals of these components are the same.

Same components of 1 on the first end 1004 and on the second end area 2004 are denoted by like reference numerals, but in the second end region 2004 the input shaft 3 the relevant reference numerals additionally provided with an apostrophe '.

The storage of the first secondary shaft 62 has a ball bearing 65 as a fixed bearing and a roller bearing 66 as a floating bearing. The storage of the second secondary shaft 67 has a ball bearing 69 as a fixed bearing and a roller bearing 68 as a floating bearing.

On the input shaft 3 is in the first end area 1004 a first hollow shaft 1029 intended. The first hollow shaft 1029 is on the input shaft 3 with radial bearings 1063 and 1064 and between a first thrust bearing 1045 and a second thrust bearing 1055 stored. On the first hollow shaft 1029 are a first fixed bike 41 and a second fixed wheel 42 arranged.

In the second end area 2004 is a second hollow shaft 2029 arranged. The second hollow shaft 2029 is on the input shaft 3 with radial bearings 2063 and 2064 and axially between a third thrust bearing 2045 and the fourth thrust bearing 2055 stored. On the second hollow shaft 2029 are a third Festrad 43 and a fourth fixed wheel 44 arranged.

On the first hollow shaft 1029 is still a fifth idler 35 arranged. The fifth idler wheel 35 is on a radial bearing 1070 and between thrust bearings 1097 and 1098 stored. Accordingly, on the second hollow shaft 2029 a sixth idler gear 36 on a radial bearing 2070 and between thrust bearings 2097 and 2098 stored.

On the first spur 62 are one with the first fixed wheel 41 combing first idler gear 31 on a radial bearing 1075 and one with the fourth fixed wheel 44 combing fourth idler gear 34 on a radial bearing 2075 arranged. Between the first idler gear 31 and the fourth idler gear 34 is a double-acting first external shift sleeve 1005 on the first auxiliary shaft 62 arranged.

On the first spur 62 is still one with the fifth idler gear 35 Combining fifth wheel 45 and one with the sixth idler gear 36 Combining sixth wheel 46 arranged. With the first spur 62 is a first output pinion 51 firmly connected, which meshes with a ring gear of a differential, not shown here.

On the second spur 67 are one with the second fixed wheel 42 meshing second idler gear 32 on a radial bearing 1575 and one with the third fixed wheel 43 meshing third idler gear 33 on a radial bearing 1575 arranged. Between the second idler gear 32 and the third idler gear 33 is a double-acting second external shift sleeve 1505 on the second secondary shaft 67 arranged.

With the second spur 67 is still a second output pinion 52 firmly connected, which meshes with the ring gear of the differential, not shown here.

A gear a becomes the fifth idler gear 35 and the fifth fixed wheel 45 educated. A gear b will be with the first idler gear 31 and the first fixed wheel 41 educated. A gear c is with the second idler gear 32 and the second fixed wheel 42 educated. A gear d becomes the sixth idler gear 36 and the sixth fixed wheel 46 educated. A gear e becomes the fourth idler gear 34 and the fourth fixed wheel 44 educated. A gear f becomes with the third loose wheel 33 and the third fixed wheel 43 educated.

The loose wheels have helical gears 73 on, which mesh with helical gears of the fixed wheels, such as 2 shows in more detail.

In the area of the first end area 1004 the input shaft 3 is a first friction clutch assembly 1006 with a first multi-plate clutch 1016 arranged. An outer plate carrier 1017 the first multi-plate clutch 1016 is with the input shaft 3 firmly connected. An inner plate carrier 1018 the first multi-plate clutch 1016 is with the first hollow shaft 1029 rotatably connected.

To operate the first friction clutch assembly 1006 is a first clutch axial actuator 1007 intended. The first clutch axial actuator 1007 has a first actuating element 1012 with a first drive toothing 1035 on. The first drive toothing 1035 is about a first idler 1030 a first external sliding sleeve Axialbetätigungseinheit 1008 in operative connection with a first drive 1025 ,

The first idler 1030 is on a first actuation shaft 1095 with a symmetry axis 1099 provided on the a first external shift drum 1010 axially fixed but in the circumferential direction via a not shown here toothing with respect to the housing 28 is freely movable. The first external shift drum 1010 has a first external control groove 1009 in which a first external switching pin 1011 is slidably disposed. The first external shift drum 1010 is with the rotating idler 1030 rotatably connected.

The first external switching pin 1011 is operatively connected to a shift fork select actuator 1093 , in turn, in selective operative connection with the first external shift sleeve 1005 and the second external shift sleeve 1505 stands.

In the area of the second end area 2004 the input shaft 3 is a second friction clutch assembly 2006 with a second multi-plate clutch 2016 arranged. An outer plate carrier 2017 the second multi-plate clutch 2016 is with the input shaft 3 firmly connected. An inner plate carrier 2018 is with the second hollow shaft 2029 rotatably connected.

To operate the second friction clutch assembly 2006 is a second clutch axial actuator 2007 intended. The second clutch axial actuator 2007 has a second actuator 2012 with a second drive toothing 2035 on. The second drive toothing 2035 is about a second idler 2030 with a second external sliding sleeve Axialbetätigungseinheit 2008 in operative connection with a second drive 2025 ,

The second idler 2030 is on a second actuation shaft 2095 with a second axis of symmetry 2099 provided on the second external shift drum 2010 axially fixed, but freely movable in the circumferential direction. The second external shift drum 2010 has a second external control groove 2009 in which a rotationally fixed, but axially freely movable second external Schaltpin 2011 is slidably disposed.

How to get in 2 Good, falls the axis of symmetry of the second shift drum 2010 with the symmetry axis 2099 of the second intermediate gear 2030 and the second operating shaft 2095 together. As you can see here well, the second external Steuerut is divided 2009 in three sections 2013 . 2014 and 2015 ,

The second switching pin 2011 is operatively connected to the shift fork selecting actuator 1093 , in turn, in selective operative connection with the first external shift sleeve 1005 on the first auxiliary shaft 62 and the second external shift sleeve 1505 on the second secondary shaft 67 stands.

2 shows the second clutch and synchronizer 2001 out 1 in an enlarged view.

The second coupling and synchronization device 2001 acts via the shift fork selector actuator 1093 with the first external shift sleeve 1005 on the first auxiliary shaft 62 and the second external shift sleeve 1505 on the second secondary shaft 67 over here and in 1 not shown shift forks together.

As you can see here very well, is the first external shift sleeve 1005 on the first auxiliary shaft 62 as a double-sided sliding sleeve 1005 educated. The first external shift sleeve 1005 has an internal toothing 1050 axially displaceable with external teeth 1072 a first hub 1096 engaged. The first hub 1096 is fixed with the first secondary shaft 62 connected. The first external shift sleeve 1005 can be based on the neutral position shown here via a first synchronizer ring 1053 either with the synchronization toothing 1039 a first gearing 1078 of the first loose wheel 31 or via a second synchronizer ring 2053 with a second gearing 2078 of the fifth loose wheel 35 get connected.

In the neutral position shown here is the first external shift sleeve 1005 neither with the first gearing 1078 of the first loose wheel 31 still with the second gearing 2078 of the fifth loose wheel 35 engaged.

The second drive 2025 is designed as an electric motor with a worm drive.

How to get in 1 looks good, acts the first friction clutch assembly 1006 with the first clutch axial actuator 1007 together, in turn, mechanically with a first sliding sleeve Axialbetätigungseinheit 8th is in operative connection or mechanically coupled with this. Accordingly, on the second end portion 2004 the input shaft 3 a second clutch axial actuator 2007 with a second shift sleeve Axialbetätigungseinheit 8th' arranged.

A first internal shift sleeve 5 is in the first end area 1004 the input shaft 3 arranged and standing in 1 on a neutral shift position in front of a shift toothing of the fifth idler gear, not shown here 31 without engaging it.

A second internal shift sleeve 5 ' is in the second end region 2004 the input shaft 3 arranged and she stands in 1 on a neutral switch position in front of a best in 2 to see switching teeth 2079 of the sixth idler gear 36 without engaging it.

In the 2 shown end portions of the internal shift drum 10 ' and analogously, the front areas of the other internal shift drum 10 be from the respectively assigned internal shift sleeve 5 . 5 ' laterally bordered, wherein the edges in turn as an axial driver with respect to the shift rollers 10 . 10 ' act. The first shift sleeve 5 encloses thereby the first shift drum 10 and the second shift sleeve 5 ' encloses thereby the second shift drum 10 ' , whereby it is axially guided relative to the respective shift drum, but in the circumferential direction with respect to this is rotatable.

From the first actuator 1012 protrudes radially inward a first internal switching pin 11 out in a first internal control groove 9 the first internal shift drum 10 is slidably disposed. The first internal shift drum 10 is opposite the gearbox 28 axially displaceable and rotationally fixed to the housing 28 on the first internal shift sleeve 5 arranged. The first internal shift drum 10 has for this purpose an external toothing, not shown here, or another rotary fixing to the housing, which has an internal toothing, not shown here, of the gear housing 28 or another rotational fixation to the transmission housing 28 engaged.

How to best in 2 sees, protrudes from the second actuator 2012 radially inward a second internal switching pin 11 ' out in a second internal control groove 9 ' the second internal shift drum 10 ' is slidably disposed. The second internal shift drum 10 ' is opposite the gearbox 28 axially displaceable and rotationally fixed to the housing 28 on the second internal shift sleeve 5 ' arranged. The second internal shift drum 10 ' has for this purpose an external toothing, not shown here, which is not shown here with an internal toothing of the transmission housing 28 engaged.

2 shows the second multi-plate clutch 2016 in more detail. The outer plate carrier 2017 is with the input shaft 3 firmly connected. The inner plate carrier 2018 is on a ring heel 2087 of the outer disc carrier 2017 the input shaft 3 stored, via a radial bearing 2049 ,

Slats of an outer disc pack 2019 are in an outer lamellar toothing 2037 in the outer plate carrier 2017 guided axially displaceable. The slats of an inner plate pack 2020 are axially displaceable in an internal lamellar toothing in the inner plate carrier 2018 guided. The slats of the outer disk pack 2019 and the blades of the inner disc pack 2020 lie against each other and are in a closed position of the second multi-plate clutch 2016 from a printing plate 2021 acted upon axially.

The printing plate 2021 is about a thrust bearing 2024 and a thrust bearing ring 2036 with an actuating ball designed as an actuating body 2023 in active connection.

The actuator body 2023 is between one on the gearbox 28 arranged ramp structure 2058 and a thrust bearing ring 2036 a thrust bearing 2024 arranged.

As you can see here, the second drive gearing meshes 2035 of the second actuating element 2012 with the teeth of the second intermediate gear 2030 , In this case, the second actuating element 2012 by means of a thrust bearing 2048 and a thrust bearing 2047 in the transmission housing 28 pivoted.

In 2 is still good to see that the inner plate carrier 2018 the second multi-plate clutch 2016 permanently fixed to the second hollow shaft 2029 connected is.

In the in 2 shown neutral position is the second internal shift sleeve 5 ' via its internal toothing with an outer toothing of the inner disk carrier 2018 engaged. The second internal shift sleeve 5 ' can via a synchronous ring 53 ' with a gearing 2079 of the idler wheel 36 be engaged.

3 shows a plan view of a peripheral portion 2077 the second external shift drum 2010 from the 1 and 2 , with the second external control groove 2009 the second external sliding sleeve Axialbetätigungseinheit 2008 , The second external control groove 2009 has three sections, namely a sloping first section 2013 , a straight second section 2014 and a straight third section 2015 , The straight sections 2014 and 2015 the second external control groove 2009 have no axial extent, they are parallel to edges 2091 and 2092 of the peripheral portion 2077 arranged.

The second external switching pin 2011 follows the second external control groove 2009 in the axial direction, the axially fixed rotational movements of the second external shift drum 2010 on the second axis of symmetry 2099 of the second intermediate gear 2030 arranged and connected to this. It takes the second external Schaltpin 2011 five switch positions "1", "2", "3", "4" and "5". A first neutral shift position "1" is at a transition from the oblique first portion 2013 to the second straight second section 2014 already planned. The second switching position "2" lies in the second section 2014 , The third shift position "3" is at the end of the second section 2014 , The fourth shift position "4" is at a transition from the first section 2013 to the third section 2015 provided, and the fifth switching position "5" is at the end of the third section 2015 , The second external switching pin 2011 may vary depending on the circumferential shift positions "1" to "5" of the second external shift drum 2010 in the direction of arrow C or D back and forth.

This axial movement is via the shift fork selector actuator 1093 and a shift fork, not shown here on the preselected first external shift sleeve 1005 on the first auxiliary shaft 62 or on the preselected second external shift sleeve 1505 on the second secondary shaft 67 transfer.

4 shows a plan view of a peripheral portion 77 ' the second internal shift drum 10 ' from the 1 and 2 , with the second internal control groove 9 ' the second internal shift sleeve axial actuator 8th' , The second internal control groove 9 ' has three sections, namely a sloping first section 13 , a straight second section 14 and a straight third section 15 , The straight sections 14 and 15 the second internal control groove 9 ' are parallel to edges 91 ' and 92 ' of the internal peripheral portion 77 ' the second internal shift drum 10 ' arranged and have no axial extent.

The second internal shift drum 10 ' with the second internal control groove 9 ' follows axially the axially fixed but rotationally free movements of the second internal switching pin 11 ' , It takes the second internal Schaltpin 11 ' five switch positions "1", "2", "3", "4" and "5". A first neutral shift position "1" is at a transition from the oblique first portion 13 to the straight third section 15 intended. The second switching position "2" is at the transition of the first section 13 to the second section 14 , The third shift position "3" is at the end of the second section 14 , The fourth shift position "4" is already within the third section 2015 , and the fifth shift position "5" is at the end of the third section 2015 , The second internal shift drum 10 ' can move back and forth in the direction of arrow C or D.

The second internal shift drum 10 ' stands with the only single-acting second internal shift sleeve 5 ' engaged. Corresponding to this is the third straight section 15 the second internal control groove 9 ' parallel to a border 92 ' aligned, but not near the edge 92 ' but rather in the middle of the peripheral surface shown here 77 ' , The cam has no axial extent in this section.

5 shows a plan view of a ramp structure 2058 the second clutch axial actuator 2007 and the internal shift sleeve axial operation. As you can see here well, the symmetry axis of the second actuator falls 2012 with the symmetry axis 57 the input shaft 3 together.

The three sections 13 . 14 and 15 the second internal control groove 9 ' in 4 correspond in this plan view of the second actuator 2012 with the housing fixed ramp structure underneath 2058 Swivel angle ranges of the second actuating element 2012 , The five switching positions "1", "2", "3", "4" and "5" correspond to five angular positions which the second actuating element 2012 with the total of three distributed on the circumference of actuators 2023 can take.

The actuator body 2023 are here spherical and are in each case in two directions on ramp-shaped actuating contours 2022 the ramp structure 2058 guided. In the neutral switching position "1" shown here, the actuating contours 2022 in each case the lowest position of the respective ramp structure 2058 in relation to the drawing plane. This lowest position extends between the switching position "2" and "4" of the second internal shift drum 10 ' , like it 5 shows. Toward the shift position "3" in the second section 14 or toward the shift position "5" in the third section 15 Be the actuator body on the ramp structure 2058 out in the direction out of the drawing plane.

The second actuator 2012 has a drive toothing in a limited circumferential area 2035 on. The drive toothing 2035 extends at least over a peripheral region corresponding to the angle between switching position "3" and "5".

As in 5 Good to see are when pivoting the second actuator 2012 for axial displacement of the second internal shift drum 10 ' due to a mechanical coupling at the same time the actuator body 2023 around the axis 57 emotional. The actuator body roll 2023 on the with the gearbox 28 connected ramp structure 2058 from. The three actuating contours 2022 have a lowest position in the ramp structure between switching positions "1" and "2" or "1" and "4" 2058 on, leaving the actuator body 2023 in this area no or only a small constant force on the thrust bearing ring 2036 exercise. Thus, the inner disc pack 2020 and the outer disc pack 2019 as in the 1 and 2 shown, detached from each other.

The second internal switching pin 11 ' moves from a middle neutral shift position "1", as it 4 shows, on a straight track in the second internal control groove 9 ' , If the second internal switching pin 11 ' in the first sloping section 2013 is moved in the direction of the shift position "2", moves due to the inclined formation of the second internal cam groove 9 ' the second internal shift drum 10 ' axially in the direction of arrow C, and it takes the second internal shift sleeve 5 ' with, so that, for example, after synchronizing the speeds of the inner disc carrier 2018 a positive connection between the inner plate carrier 2018 and the sixth idler 36 is made.

Here is the internal toothing of the second internal shift sleeve 5 ' via the toothing of the synchronizer ring 53 ' on the gearing 2079 of the sixth idler gear 36 pushed.

Another pivoting of the second actuating element 2012 through the drive toothing 2035 in the position "3" in 4 causes due to the design of the second internal Steuerut 9 ' no further axial movement of the second shift drum 10 ' more, but only one actuation of the friction clutch assembly 2006 ,

The friction clutch assembly 2006 is operated as follows. To transfer a torque, the disk packs 2019 and 2020 the second multi-plate clutch 2016 through the pressure plate 2021 compressed. This is the second actuator 2012 through the drive toothing 2035 pivoted so in the position "3" that the actuator body 2023 on the actuating contour 2022 the one with the gearbox 28 firmly connected ramp structure 2058 rolls.

When rolling on the actuating contour 2022 the ramp structure 2058 will the operating body 2023 moved axially such that the actuating body 2023 over the thrust bearing ring 2036 , the thrust bearing 2024 and over the pressure plate 2021 a contact pressure on the inner lamellae of the inner plate pack 2020 and on the slats of the outer disc pack 2019 exercise. To release the frictional connection between the slats of the inner plate pack 2020 and the fins of the outer disc pack 2019 becomes the second actuator 2012 through the drive toothing 2035 so pivoted back to its initial position "2" that the actuator body 2023 no longer exert any axial force on the coupling.

In the other direction, the coupling and synchronizing device works 2001 similar. Will the internal switching pin 11 ' due to actuation of the second actuator 2012 moves from its shift position "1" towards the shift position "4" and then to "5", then moves the second internal shift drum 10 ' not in the axial direction. From the switching position "4" begins a pivoting of the second actuating element 2012 in the switching position "5" and then causes a closing of the second friction clutch assembly 2006 similar to the above-described movement from the shift position "2" to the shift position "4".

The five in 4 shown switching positions "1", "2", "3", "4" and "5" can be achieved that a as in 2 shown second intermediate 2030 , which is driven by an electric motor with worm drive, in the drive toothing 2035 engages and the second actuator 2012 around the axis 57 adjusted.

6 shows the second clutch Axialbetätigungseinheit 2007 with the second internal shift sleeve axial actuator 8th' in cross section, wherein the second internal Schaltpin 11 ' in switch position "1".

7 . 8th . 9 and 10 show corresponding views of the second external sliding sleeve Axialbetätigungseinheit 2008 and the second internal shift sleeve axial actuator 8th' and the second clutch axial actuator 2007 in the neutral switching position "1". In this switching position is the second internal Schaltpin 8th' or the second external switching pin 2011 in a transition between the first section 13 respectively. 2013 and the second section 15 respectively. 2014 the second internal control groove 9 ' or the second external control groove 2009 the second internal shift drum 10 ' or the second external shift drum 2010 are arranged. The second external shift drum 2010 and the second internal shift drum 10 ' are in a middle position.

11 . 12 . 13 and 14 show corresponding views of the second external sliding sleeve Axialbetätigungseinheit 2008 and the second internal shift sleeve axial actuator 8th' and the second clutch axial actuator 2007 in the switching position "2". In this switching position are the second external Schaltpin 2011 or the second internal switching pin 11 ' at the transition from the oblique first section 13 and 2013 and in the middle of the straight section 2014 the second internal control groove 9 ' or the second external control groove 2009 arranged. The second internal shift drum 10 ' is shifted relative to the middle position to the left in the direction of arrow C, as 14 shows. The second external shift drum 2010 is due to the design of the second external Steuerut 2009 as before in the middle position according to 7 ,

15 . 16 . 17 and 18 show corresponding views of the second external sliding sleeve Axialbetätigungseinheit 2008 and the second internal shift sleeve axial actuator 8th' and the second clutch axial actuator 2007 in the switching position "3". In this switching position are the external switching pins 2011 respectively. 11 ' at the end of the straight second section 14 respectively. 2014 in the second internal control groove 9 ' or the second external control groove 2009 arranged. The shift drum 10 ' is shifted relative to the middle position to the left in the direction of arrow C, as 18 shows. The thrust bearing ring is shifted to the right. The second external shift drum 2010 is due to the design of the second external Steuerut 2009 as before in the middle position according to 7 and 11 ,

The 15 and 16 show a switching position "3" of the second external switching pin 2011 or the second internal switching pin 11 ' in the second external control groove 2009 or the second internal control groove 9 ' in more detail. In this switching position, the second external Schaltpin has 2011 or the second internal switching pin 11 ' almost the end of the second section 2014 respectively. 14 the second external control groove 2009 or the second internal control groove 9 ' reached. In the section 2014 respectively. 14 ' takes place with respect to the switching position "2" no further axial displacement of the second external shift drum 2010 ,

As in 18 compared to the 14 can be seen, are the actuator body 2013 raised in the switching position "3" relative to the switching position "2". In the transition from the switching position "2" to the switching position "3", the actuating balls begin 2023 a force on the second pressure plate 2021 the second multi-plate clutch 2016 exercise. The increase of the force starts only after the switching position "2" when the Synchronization phase of the internal teeth of the second internal shift sleeve 5 ' with the axial toothing 2079 of the fourth idler gear 34 is completed.

In switch position "3" are the actuator body 2023 by the rotation of the second actuating element 2012 in the direction of arrow D - see 17 - in a switching position in which they have a large force on the pressure plate 2021 the second multi-plate clutch 2016 exercise. This is also in 18 shown in the distance a between the thrust bearing ring 2036 and on the transmission housing 1128 fixed ramp structure 2058 opposite to the illustration in 14 has become larger.

19 . 20 . 21 and 22 show corresponding views of the second external sliding sleeve Axialbetätigungseinheit 2008 and the second internal shift sleeve axial actuator 8th' and the second clutch axial actuator 2007 in the switching position "4". In this switching position "4" is the second external switching pin 2011 at the transition from the oblique first section 2013 to the straight section 2015 the second external control groove 2009 , The second internal shift drum 10 ' is in the neutral position and has not moved. In the section 2013 respectively. 13 is opposite to the shift position "2" an axial displacement of the second external shift drum 2010 to the right in the direction of the arrow "D".

This axial movement of the switch pin 2011 External shift sleeve axial actuation is via the shift fork selector actuator 1093 and a shift fork, not shown here on the preselected first external shift sleeve 1005 on the first auxiliary shaft 62 or on the preselected second external shift sleeve 1505 on the second secondary shaft 67 transfer.

23 . 24 . 25 and 26 show corresponding views of the second external sliding sleeve Axialbetätigungseinheit 2008 and the second internal shift sleeve axial actuator 8th' and the second clutch axial actuator 2007 in the switching position "5", in which the second external Schaltpin 2011 at the end of the third section 2015 located. The second internal shift drum 10 ' has remained in the middle position since the second internal tax credit 9 ' in the middle of the internal shift drum 10 ' in the third section 15 runs centrally and straight. The second external shift drum 2010 is in the same axial position as in 19 shown switching position "4".

Similar to 18 are located in the switching position "5" the actuator body 2023 by the rotation of the second actuating element 2012 in the direction of arrow C in a switching position in which they exert a large force on the pressure plate 2021 the second multi-plate clutch 2016 exercise. This is also in 26 shown in the distance between the thrust bearing ring 2036 and on the transmission housing 1128 fixed ramp structure 2058 opposite to the illustration in 22 has become larger.

Depending on the direction of rotation, either the inner shift sleeve is actuated via the inner shift sleeve axial actuation or an outer shift sleeve via the outer shift sleeve axial actuation. The actuation of the coupling is independent of the direction of rotation via the axial coupling operation.

In the in the 1 to 26 shown switching arrangement 101 with the first friction clutch assembly 1006 and the second friction clutch assembly 2006 can via the first clutch axial actuator 1007 and via the second clutch axial actuator 2007 in cooperation with the first external sliding sleeve Axialbetätigungseinheit 1008 , the first internal shift sleeve axial actuator 8th and with the second external shift sleeve axial actuator 2008 and the second internal shift sleeve axial actuator 8th' six torque ratios with the gears a, b, c, d, e and f are switched. This is subsequently in each case starting from the neutral position in the 1 and 2 described.

To insert gear a is first the first actuator 1012 around the axis 57 pivoted. This meshes with the drive teeth 1035 of the first actuating element 1012 with the first idler 1030 that from the first drive 1025 is driven. This is the first internal shift drum 10 with the first internal gearshift sleeve 5 from the neutral shift position "1" in the direction of the shift teeth of the fifth idler gear 35 shifted to the switching position "2".

The fifth idler wheel 35 is in switch position "2" with its gear teeth via the first internal gearshift sleeve 5 positively with the first inner plate carrier 1018 connected and the coupling process begins. The spherical actuator body roll 1023 on the ramp structure 1058 in the direction of the switching position "3" and exert an increasing contact pressure on the pressure plate 1021 the first multi-plate clutch 1016 from, until a frictional engagement in the first multi-plate clutch 1016 is reached and the engagement of the gear a between the fifth idler gear 35 and the fifth fixed wheel 45 in the switching position 3 is completed.

The power flow for the gear a runs after closing the first multi-plate clutch 1016 from the input shaft 3 over the outer plate carrier 1017 , about the outer Lammellenpaket 1019 and the inner disc pack 1020 , the first internal shift sleeve 5 , the gear teeth of the fifth idler gear 35 and via the helical gearing to the fifth fixed gear 45 and about the first spur 62 to the first output pinion 51 ,

To insert gear b is first the first actuator 1012 around the axis 57 pivoted.

The axially fixed external and pivotable first external shift drum 1010 shifts the axially movable first external switching pin 1011 and thus - selected by the first shift fork selector actuator 1093 - With a shift fork, not shown here, the first external shift sleeve 1005 on the first auxiliary shaft 62 until the synchronization is completed and the spline 1050 the first external shift sleeve 1005 with the gearing 1978 of the first idler gear 31 on the first auxiliary shaft 62 engaged.

By further pivoting of the first actuating element 1012 becomes the first multi-plate clutch 1016 closed as described above.

The power flow runs after closing the first multi-plate clutch 1016 from the input shaft 3 over the first outer plate carrier 1017 , about the first outer Lammellenpaket 1019 and the first inner disc pack 1020 on the first inner plate carrier 1018 and from there over the first hollow shaft 1029 on the first fixed wheel 41 , The first fixed wheel 41 directs the power flow over his with the first idler gear 31 meshing helical gearing to the first secondary shaft 62 that the power flow to the first output pinion 51 supplies.

To insert gear c is the first actuator 1012 around the axis 57 pivoted.

The axially fixed, pivotable first external shift drum 1010 shifts the only axially movable first shift pin 1011 on the actuating shaft 1095 and thus - selected by the first shift fork selector actuator 1093 - With a shift fork, not shown here, the second external shift sleeve 1505 on the spur 67 until the synchronization is complete and the spline of the first external shift sleeve 1505 with the gear teeth of the second idler gear 32 on the second secondary shaft 67 engaged.

By further pivoting the first actuating element 1012 becomes the first multi-plate clutch 1016 closed as described above.

The power flow runs after closing the first multi-plate clutch 1016 from the input shaft 3 over the first outer plate carrier 1017 , about the first outer Lammellenpaket 1019 and the first inner disc pack 1020 on the first inner plate carrier 1018 and from there over the first hollow shaft 1029 on the second fixed wheel 42 , The second fixed wheel 42 directs the power flow over his with the second idler gear 32 meshing helical gearing to the second auxiliary shaft 67 that the power flow to the second output pinion 52 supplies.

To engage gear d, the second actuator 2012 around the axis 57 pivoted.

This is the second internal shift drum 10 ' with the second internal shift sleeve 5 ' from the in 4 shown neutral shift position "1" in the direction of the gear teeth of the sixth idler gear 36 shifted to the switching position "2".

The sixth idler 36 is in the switching position "2" with its gear teeth 2079 via the second internal shift sleeve 5 ' positively with the second inner plate carrier 2018 connected and the coupling process begins. The spherical actuator body roll 2023 on the ramp structure 2058 in the direction of the switching position "3" and exert an increasing contact pressure on the pressure plate 2021 the second multi-plate clutch 2016 off, until a frictional engagement in the second multi-plate clutch 2016 is reached and the engagement of gear d between the sixth idler gear 36 and the sixth fixed wheel 46 in the switching position 3 is completed.

The power flow runs after closing the second multi-plate clutch 2016 from the input shaft 3 over the second outer plate carrier 2017 , about the second outer Lammellenpaket 2019 and the second inner disc pack 2020 , the second internal shift sleeve 5 ' , the shift teeth 2079 of the sixth idler gear 36 and via the helical gearing with the sixth fixed gear 46 and about the first spur 62 to the first output pinion 51 ,

To insert gear e is the second actuator 2012 around the axis 57 pivoted by the second drive 2025 the second idler 2030 drives, its teeth with the second drive toothing 2035 of the second actuating element 2012 engaged.

The axially movable second external switching pin 2011 shifts due to its rotation of the axially fixed and rotationally freely movable second external shift drum 2010 and - selected by the first shift fork preselection actuator 1093 - With a shift fork, not shown here, the first external shift sleeve 1005 in the direction of arrow C until the synchronization is completed and the axial gearing 1050 the first external shift sleeve 1005 with the gearing of the fourth idler gear 34 engaged.

By further pivoting of the second actuating element 2012 becomes the second multi-plate clutch 2016 closed.

The power flow runs after closing the second multi-plate clutch 2016 from the input shaft 3 over the first outer plate carrier 2017 , about the first outer Lammellenpaket 2019 and the first inner disc pack 2020 on the first inner plate carrier 2018 and from there via the second hollow shaft 2029 on the fourth fixed wheel 44 , The fourth fixed wheel 44 directs the power flow over his with the fourth idler gear 34 meshing helical gearing to the first secondary shaft 62 that the power flow to the first output pinion 51 supplies.

To insert gear f is the second actuator 2012 around the axis 57 pivoted by the second drive 2025 the second idler 2030 drives, its teeth with the second drive toothing 2035 of the second actuating element 2012 engaged.

The axially movable and rotationally fixed second external Schaltpin 2011 displaced by the rotation of the axially fixed and rotationally movable second external shift drum 2010 Selected by the first shift fork preselector actuator 1093 - With a shift fork, not shown here, the second external shift sleeve 1505 on the second secondary shaft 67 in the direction of arrow C, until the synchronization is completed and the axial toothing of the second external shift sleeve 1505 on the second secondary shaft 67 with the gear teeth of the third idler gear 33 engaged.

By further pivoting the first actuating element 1012 becomes the second multi-plate clutch 2016 closed.

The power flow runs after closing the second multi-plate clutch 2016 from the input shaft 3 over the second outer plate carrier 2017 , about the second outer Lammellenpaket 2019 and the second inner disc pack 2020 on the second inner plate carrier 2018 and from there via the second hollow shaft 2029 on the third fixed wheel 43 , The third fixed wheel 43 directs the power flow over his with the third idler gear 33 meshing helical gearing to the second auxiliary shaft 67 that the power flow to the second output pinion 52 supplies.

27 shows a diagram with the course of the axial movement of the second internal shift sleeve 5 ' like it 8th . 12 and 16 show, compared to the course of an on an actuator body 2023 of the second actuating element 2012 acting axial force when switching a gear. The graph A represents the course of the axial movement of the second internal shift sleeve 5 ' while graph B shows the axial force on the actuators 2023 shows. In the direction of the ordinate, the respective force or the respective path is plotted and in the direction of the abscissa the time t.

At time t = t ₀ is the second internal switching pin 11 ' in the neutral switching position "1". From the time t ₀ takes on the axial displacement of the second internal shift sleeve 5 ' due to the movement of the second shift drum 10 ' to, as the graph A shows. The axial force, by means of the actuating contour 2022 on the actuating ball 2023 acts, remains in this time interval from t ₀ to t ₁ zero, ie there is no force on the actuator body 2023 ,

Upon reaching the time t ₁ in the switching position "2" ends the axial displacement of the second internal shift sleeve 5 ' as shown in Graph A. The axial force on the actuator body 2023 On the other hand, it is growing because with the switching position "2" at the time t _1, a ramp area of the actuating contour 2022 is reached. The axial force of the actuator body 2023 on the printing plate 2021 increases until in switching position "3" at time t ₂ a target value is reached.

28 shows a diagram of the torque transfer during the load change of the first friction clutch assembly 1006 on the second friction clutch assembly 2006 and the course of release and engagement of gears "a" and "d", those of the first and second friction clutch assemblies 1006 respectively. 2006 assigned. The torque transmission of the first friction clutch assembly 2006 is shown as a function of the time t with the solid line graph A, and the torque transmission of the second friction clutch assembly 2006 is shown as a function of time t with graph B in solid line. The movement of the first internal shift sleeve 5 is shown as a function of the time t with the graphs C in dashed line, and the movement of the second internal shift sleeve 5 ' is shown as a function of the time t with the graphs D in dashed line.

At time t ₀ is the first friction clutch assembly 1006 that is, not frictionally engaged, and does not transmit torque as graph A shows because there is no appreciable force from the actuator body 1023 on the first printing plate 1021 is exercised. The first internal shift drum 10 with the first internal gearshift sleeve 5 is at this time t ₀ in the neutral switching position "1". The process of engaging a gear a begins, as the graph C shows, and it is completed at time t ₁ when the first internal shift sleeve 5 has reached the switching position "4".

At time t ₀ is the second friction clutch assembly 2006 closed and it transmits the full torque, as Graph D shows. The second internal shift sleeve 5 ' is during the entire time interval from t ₀ to t ₁ in the switching position "3", so that the full torque on the sixth fixed gear 46 is transmitted.

At time t ₁ , a reduction of the torque transmission of the second friction clutch assembly begins 2006 while the torque transmission of the first friction clutch assembly 1006 already increases, as shown by the graphs A and B in the time interval between t ₁ and t ₂ . At the same time goes the second internal shift drum 10 ' with the second internal shift sleeve 5 ' from the shift position "3" to the shift position "2" via, but without designing the gear d. Only when the switching position "2" is left at the time t ₂ , the layout of the gear d starts in the switching position "1". This allows stepless switching and coupling between gears d and a.

The switching arrangement described basically works with only a single secondary shaft, although here a transmission with two auxiliary shafts is shown.

The actuator body 2023 in the 1 to 26 is radial clearance in the actuator 2012 to ensure a good function. The spherical actuator body 2023 also roll in a circumferential contour in the thrust bearing ring 2036 formed as a circumferential groove.

For rotary coupling of the hollow shafts with the respective inner disc carrier, axial toothing is to be preferred.

In the embodiment described above, it should be emphasized that the internal shift drum is axially fixed with respect to the shift sleeve, but rotatable thereto.

29 shows of a switching arrangement 102 a gearbox 2 According to a second embodiment of the invention, establishing a second coupling and synchronization 2001 ,

The switching arrangement 102 differs from the second clutch and synchronizer 2001 the first embodiment of the invention as shown in the 1 to 26 will be shown. One difference is that instead of the two-sided external shift sleeves 1005 respectively. 1505 a unilaterally acting first external shift sleeve 2005 and a single-acting second external shift sleeve 2505 on the first auxiliary shaft 62 and the second secondary shaft 67 are arranged.

The single-acting first external shift sleeve 2005 and the single-acting second external shift sleeve 2505 via associated external shift drum in conjunction with shift fork preselection actuators, of which in 29 a second shift fork preselector actuators 2093 is shown, operated.

The other components shown have the same functions as in the preceding 1 to 26 and are marked accordingly with the same reference numerals.

The direction of the axial displacement of the sliding sleeve depends on the wheel arrangement, in principle this can be done in both directions.

30 shows a motor vehicle 80 with an engine block 81 and a powertrain 82 , A gearbox 2 with a gear housing not shown here and a clutch and synchronizer according to the preceding figures is in a rear portion of the engine block 81 coupled. The drive train 82 has a cardan shaft 83 and a differential gear 84 to drive the rear wheels 85 on.

A gearshift lever 86 is in operative connection with the transmission 2 for insertion and decoupling of aisles. An engine torque is transmitted by means of the transmission 2 with mechanically coupled coupling and synchronization device translated into a drive torque and the cardan shaft 83 that, differential gear 84 and drive shafts 94 the rear wheels 85 fed.

In an embodiment not shown here, the transmission is from the 1 and 2 used in a vehicle with front-wheel drive, with two drive shafts driving the front wheels from the differential.

Alternatively, the front wheels of a - not shown here - vehicle driven by means of a correspondingly equipped transmission, which is equipped with at least one switching arrangement of the type described above. It basically does not matter whether the transmission shafts are arranged longitudinally or transversely to the direction of travel of the vehicle.

Claims (15)

Switching arrangement for a shiftable transmission ( 2 ), comprising: - an input shaft ( 3 ), - A mounted on the input shaft hollow shaft ( 1070 ) with a first fixed wheel ( 41 ) - a secondary wave ( 62 ) with one on the secondary shaft ( 62 ) provided first idler gear ( 31 ), with the first fixed wheel ( 41 ) is engaged, - an external shift sleeve ( 1005 ) for releasably positive connection of the first idler gear ( 31 ) with the secondary shaft ( 62 ), wherein the external shift sleeve ( 1005 ) is axially movable due to actuation between a first position and a second position, - a friction clutch assembly ( 1006 ) for connecting the input shaft ( 3 ) with the hollow shaft ( 1070 ), with a clutch axial actuation unit ( 1007 ), wherein the friction clutch assembly ( 1006 ) a releasable frictional connection of the input shaft ( 3 ), with the hollow shaft ( 1070 ), - an external shift sleeve axial actuation unit ( 1008 ) for actuating the external sliding sleeve ( 1005 ), wherein the clutch axial actuation unit ( 1007 ) and an external sliding sleeve Axialbetätigungseinheit ( 1008 ) are mechanically connected to each other, wherein the clutch axial actuation unit ( 1007 ) and the external sliding sleeve Axialbetätigungseinheit ( 1008 ) are further configured so that the friction clutch assembly ( 1006 ) the frictional connection between the input shaft ( 3 ) and the hollow shaft ( 1029 ) after the external shift sleeve ( 1005 ) occupies the second position, and that the friction clutch assembly ( 1006 ) the frictional connection between the input shaft ( 3 ) and the hollow shaft ( 1029 ) before the external sliding sleeve ( 1005 ) leaves the second position to take the first position, and further - one on the input shaft ( 3 ) provided second loose wheel ( 35 ), with a second fixed wheel ( 35 ) is engaged, - an internal shift sleeve ( 5 ) for the releasable positive connection of the second idler gear ( 35 ) with the input shaft ( 3 ), whereby the internal shift sleeve ( 5 ) is axially movable due to actuation between a first position and a second position, - wherein the friction clutch assembly ( 1006 ) a releasable frictional connection of the input shaft ( 3 ) with the internal gearshift sleeve ( 5 ), - an internal shift sleeve axial actuation unit ( 8th ) for actuating the internal shift sleeve ( 5 ), wherein the clutch axial actuation unit ( 1007 ) and the internal shift sleeve axial actuator ( 8th ) are mechanically connected to each other, further wherein the clutch axial actuation unit ( 1007 ) and the internal shift sleeve axial actuator ( 8th ) are formed so that the friction clutch assembly ( 1006 ) the frictional connection to the internal shift sleeve ( 5 ) after the internal shift sleeve ( 5 ) occupies the second position, and that the friction clutch assembly ( 1006 ) the frictional connection of the internal sliding sleeve ( 5 ) with the input shaft ( 3 ) releases before the internal shift sleeve leaves the second position to assume the first position, wherein the external shift sleeve Axialbetätigungseinheit ( 1008 ) and the internal shift sleeve axial actuator ( 8th ) are mechanically connected with each other in such a way that the internal sliding sleeve ( 5 ) is in the second position when the external shift sleeve ( 1005 ) is in the first position, and vice versa. Switching arrangement according to Claim 1, characterized in that the internal sliding sleeve axial actuating unit ( 8th ) an internal shift drum ( 10 ) and one in an internal control groove ( 9 ) of the internal shift drum ( 10 ) guided internal switching pin ( 11 ), and that the internal clutch axial actuation unit ( 8th ) a pivotable actuating element ( 1012 ), wherein the internal switching pin ( 11 ) with the pivotable actuating element ( 1012 ) connected is. Switching arrangement according to claim 1 or claim 2, characterized in that the external sliding sleeve axial actuating unit ( 1008 ) an external shift drum ( 1010 ) with an external control groove ( 1011 ) and an external switching pin ( 1011 ), wherein the external shift drum ( 1010 ) or the external switching pin ( 1011 ) via a toothing ( 1035 ) with the actuating element ( 1012 ) is engaged. Switching arrangement according to claim 2 or claim 3, characterized in that the external or internal sliding sleeve Axialbetätigungseinheit ( 1008 respectively. 8th ) are designed such that a first section of the external or internal control groove ( 1009 respectively. 9 ) of the external or internal shift drum ( 1010 respectively. 10 ) seen in the circumferential direction in a first axial portion of the external or internal shift drum ( 1010 respectively. 10 ) and that a second section of the external or internal control groove ( 1009 respectively. 9 ) of the external or internal shift drum ( 1010 respectively. 10 ) seen in the circumferential direction in a second axial portion of the external or internal shift drum ( 1010 respectively. 10 ) so that, depending on a pivoting direction of the actuating element ( 1012 ) a movement of the external or internal shift sleeve ( 1005 respectively. 5 ) in a first axial direction or a movement of the external or internal shift sleeve ( 1005 , respectively. 5 ) takes place in a second axial direction. Switching arrangement according to one of claims 2 to 4, wherein the internal shift drum ( 10 ) of the internal shift sleeve axial actuation unit ( 8th ) axially fixed and rotatable in the circumferential direction on the internal shift sleeve ( 5 ) is stored. Switching arrangement according to one of claims 2 to 5, wherein the external or internal shift drum ( 1010 respectively. 10 ) of the external or internal sliding sleeve Axialbetätigungseinheit ( 1008 respectively. 8th ) has an outer rotational attachment, which is provided for support on a housing part. Switching arrangement according to one of the preceding claims, characterized in that the friction clutch assembly ( 1006 ) a multi-plate clutch ( 1016 ) having an outer plate carrier ( 1017 ) for connection to the input shaft ( 3 ), one with the internal shift sleeve ( 5 ) associated inner plate carrier ( 1018 ), a package ( 1019 ) of the outer plate carrier ( 1017 ) received outer slats and a package ( 1020 ) of in the inner plate carrier ( 1018 ) received inner slats and a pressure plate ( 1021 ) having. Switching arrangement according to claim 7, characterized in that the coupling Axialbetätigungseinheit ( 1007 ) is formed as a clutch actuator, which is a pivotable actuator ( 1012 ), one in the range of pressure plate ( 1021 ) and actuator ( 1012 ) arranged actuating contour ( 1022 ) and one with the actuating contour ( 1022 ) cooperating actuating body ( 1023 ) for actuating the printing plate ( 1021 ) having. Switching arrangement according to Claim 8, in which the coupling axial actuating unit ( 1007 ) three actuator bodies ( 1023 ) having. Switching arrangement according to Claim 8 or Claim 9, the actuating contour ( 1022 ) is formed so that the axial extension of actuating contour ( 1022 ) and actuator body ( 1023 ) together by a movement of the actuating body ( 1023 ) is variable in the circumferential direction. Switchable transmission, comprising: - a transmission housing ( 28 ), - an input shaft ( 3 ), - a hollow shaft ( 1029 ) with a first fixed wheel ( 41 ), - a secondary wave ( 62 ) with one on the secondary shaft ( 62 ) provided first idler gear ( 31 ), with the first fixed wheel ( 41 ) is engaged, - a switching arrangement ( 101 ) according to one of the preceding claims, for the mechanically coupled to each other releasable positive connection of the first idler gear ( 31 ) with the secondary shaft ( 62 ), as well as the releasable frictional connection of the input shaft ( 3 ) with the hollow shaft ( 62 ), wherein the mechanical coupling is formed so that the frictional connection between the input shaft ( 3 ) and the hollow shaft ( 62 ) is produced after the positive connection of the first idler gear ( 31 ) with the secondary shaft ( 62 ), and wherein the frictional connection between the input shaft ( 3 ) and the hollow shaft ( 62 ) is dissolved before the positive connection of the first idler gear ( 31 ) with the secondary shaft ( 62 ), and wherein - one on the input shaft ( 3 ) provided second loose wheel ( 35 ), with a second fixed wheel ( 45 ) is engaged, - wherein the switching arrangement ( 101 ) further to the mechanically coupled releasable positive connection of the input shaft ( 3 ) with the second loose wheel ( 35 ) and for the releasable frictional connection of the input shaft ( 3 ) with the second loose wheel ( 35 ) is provided, wherein the mechanical coupling is formed so that the frictional connection between the input shaft ( 3 ) and the second loose wheel ( 35 ) is produced after the positive connection of the second idler gear ( 35 ) with the input shaft ( 3 ), and that the frictional connection between the input shaft ( 3 ) and the second loose wheel ( 35 ) is dissolved before the positive connection of the input shaft ( 3 ) with the second loose wheel ( 35 ) Is solved, further wherein the mechanical coupling is formed so that the positive connection of the first idler gear is made with the secondary shaft when the positive connection of the input shaft is solved with the second idler gear, and vice versa. Switchable transmission according to claim 11, further comprising: - a second hollow shaft ( 2029 ) with a third fixed wheel ( 43 ), - one on a side wave ( 62 ) provided third loose wheel ( 33 ), with the third fixed wheel ( 43 ) is engaged, - the switching arrangement ( 101 ) according to one of the preceding claims, for the mechanically coupled to each releasable positive connection of the third idler gear ( 33 ) with the secondary shaft ( 62 ), as well as the releasable frictional connection of the input shaft ( 3 ) with the second hollow shaft ( 2029 ), wherein the mechanical coupling is formed so that the frictional connection between the input shaft ( 3 ) and the second hollow shaft ( 2029 ) is produced after the positive connection of the third idler gear ( 33 ) with the secondary shaft ( 62 ), and wherein the frictional connection between the input shaft ( 3 ) and the second hollow shaft ( 2029 ) is solved before the positive connection of the third idler gear ( 33 ) with the secondary shaft ( 62 ) is solved, wherein further the mechanical coupling is formed so that the positive connection of the first idler gear ( 31 ) with the first secondary wave ( 62 ) is produced when the positive connection of the input shaft ( 3 ) with the second loose wheel ( 35 ), and the positive connection of the third idler gear ( 33 ) with the secondary shaft ( 62 ) is solved, that the positive connection of the first idler gear ( 31 ) with the secondary shaft ( 62 ) is solved when the positive connection of the input shaft ( 3 ) with the second loose wheel ( 35 ), and the positive connection of the third idler gear ( 33 ) with the secondary shaft ( 62 ) is solved, that the positive connection of the first idler gear ( 31 ) with the first secondary wave ( 62 ) is solved when the positive connection of the input shaft ( 3 ) with the second loose wheel ( 35 ), and the positive connection of the third idler gear ( 33 ) with the secondary shaft ( 62 ), and vice versa. A shiftable transmission according to claim 11 or claim 12, further comprising: - one on the input shaft ( 3 ) fourth idler gear provided with a fourth fixed wheel ( 46 ) is engaged, - wherein the switching arrangement ( 101 ) further to the mechanically coupled releasable positive connection of the input shaft ( 3 ) with the fourth loose wheel ( 36 ) and for the releasable frictional connection of the input shaft ( 3 ) with the fourth loose wheel ( 36 ) is provided, wherein the mechanical coupling is formed so that the frictional connection between the input shaft ( 3 ) and the fourth idler gear ( 36 ) is produced after the positive connection of the fourth idler gear ( 36 ) with the secondary shaft ( 62 ), and that the frictional connection between the input shaft ( 3 ) and the fourth idler gear ( 36 ) is dissolved before the positive connection of the input shaft ( 3 ) with the fourth loose wheel ( 36 ) is solved, wherein further the mechanical coupling is formed so that the positive connection of the first idler gear ( 31 ) with the secondary shaft ( 62 ) is produced when the positive connection of the input shaft ( 3 ) with the second loose wheel ( 35 ) is solved, and if the positive connection of the fourth idler gear ( 36 ) with the secondary shaft ( 62 ) is solved, that the positive connection of the first idler gear ( 31 ) with the secondary shaft ( 62 ) is solved when the positive connection of the input shaft ( 3 ) with the second loose wheel ( 35 ), and when the positive connection of the fourth idler gear ( 36 ) with the secondary shaft ( 62 ) is solved, that the positive connection of the first idler gear ( 31 ) with the secondary shaft ( 62 ) is solved when the positive connection of the input shaft ( 3 ) with the second loose wheel ( 35 ) is solved, and if the positive connection of the fourth idler gear ( 36 ) with the secondary shaft ( 62 ), and vice versa. Powertrain with a transmission ( 2 ) according to one of claims 11 to 13, wherein a drive shaft of the drive train ( 82 ) with an output shaft of the transmission ( 2 ) connected is. Motor vehicle ( 80 ) with a drive train ( 82 ) according to claim 14, wherein a running wheel ( 85 ) of the motor vehicle ( 80 ) with a wheel drive shaft ( 94 ) of the drive train ( 82 ) connected is.

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